Power lift of the hydraulic type



July 8, 1947. COURT 2,423,485

POWER LIFT OF: THE HYDRAULIC TYPE Filed larch 11,\1942 5 Sheets-Sheet 1 FIG. 4

INVENTOR F NK T. OOURz Jul 8, 1947. T, CO T i 2342x485" POWER LIFT OF THE 'HfD-RAULIC TYPE. v V

Filed March 11, 1942 Sheets-Sheet INVFNTOR FRANK T. COURT QM TORNEYS y 8, 1947. F. 'r. COURT 2,423,485

POWER LIFT OF THE HYDRAULIC TYPE Filed March 11, 1942 5 Sheets-Sheet 3 INVENTOR July 3, 1947. F, T COURT 2,423,485

POWER LIFT OF THE HYDRAULIC TYPE Filed March 11, 1942 5 Sheets-Sheet 4 July 8, 1947. COURT 2,423,485

POWER LIFT OF THE HYDRAULIC TYPE Filed March 11, 1942 5 Sheets-Sheet 5 412 34s I i INVENTOR' FRANK T. OOIRT Patented July 8, 1947 POWER LIFT OF THE HYDRAULIC TYPE U Frank '1. Court, Moline, Ill., assignor to Deere &

Company, Moline, 11]., a corporationoi' Illinois Application March 11, 1942, Serial No. 434,256

17 Claims.

The present invention relates generally to agricultural implements and'more particularly to a hydraulic power lift control system for agricultural implements and the like.

The object and general nature of the present invention is the provision of a hydraulic power lift for the ground working tool or other operating unit of an agricultural implement, in which is embodied a control of the working ram unit with associated automatic valve mechanism arranged so that when a given or adjustable quantity of fluid has been forced into the ram cylinder, the valve mechanism is automatically operated so as to terminate further raising, or extension of the ram unit, while locking the ram unit in extended or partially extended relation.

It is a further feature of this invention to provide an arrangement of this kind in which manually operable means is provided and which may be moved to various positions and so connected with the hydraulic system that the ram unit is automatically shifted a corresponding amount. Further, it is a feature of this invention to provide a part that can be manually set in the position of adjustment in which the ram unit is operated until the transfer of a given amount of fluid has taken place, whereupon the valve mechanism is automatically shifted back into a neutral position, terminating further adjustment of the tool and holding the latter in that I position.

These, and other objects and advantages of the present invention will be apparent to those skilled in the art after a consideration of the following detailed description, taken in conjunction with the accompanying drawings.

In the drawings:

Figure 1 is a sectional view of a tractor mounted hydraulic power lift control unit, in which the implement controlling ram is shown diagrammatically;

Figure 2 is an end view of the hydraulic power lift control unit shown in Figure 1;

Figure 3 is a fragmentary sectional view taken along the line 3-3 of Figure 1;

Figure 4 is a sectional view taken along the line 44 of Figure 1;

Figure 5 is an enlarged view of the valve mechanism, showing the valve in its raising position;

Figure 6 is a sectional view taken through a modified form of power lift hydraulic control unit;

Figure 7 is a view, partly in section, taken generally along the line l-'l of vFigure 8;

Figure 8 is a side view of the upper motion the unit shown in Figure 6, illustrating the frictionally held adjustable depth control, Figure 8 being a view taken generally along the line 8-8 of Figure 'l;

Figure 9 shows a modified form of the present invention, in which the pump and control unit may be separately mounted at any suitable point on the tractor or implement, as desired Figure 10 shows another modified form of the present invention in which the ram piston is connected directly with the valve controlling linkage;

Figure 11 is a modified form of lower valve, adapted for the modification shown in Figures 6 and 10.

Referring now to the drawings, the reference numeral I indicates in its entirety the metering cylinder or chamber and pump unit in which the principles of the presentinvention have been incorporated. The unit I is mounted on the governor housing 2 of a tractor indicated in its entirety by the reference numeral 3, and the unit I controls the flow of oil or other fluid under pressure to and from a, ram unit, which is indicated in its entirety by the reference numeral 5. The ram unit 5 includes a cylinder 6 and a piston l. The ram unit 5 is carried by a bracket 9 fixed to the axle ll of the tractor, and the piston l at its rear end is connected to an arm I2 that is secured to a rock shaft I3. The latter also has an arm l4 extending vertically and is connected-by a lift pipe 15 or other means with a ground working tool or other operating unit mounted on or connected with the tractor 3. The governor housing encloses suitable mechanism, such as a shaft or the like (not shown), by which two gears I! that comprise the principal part of a fluid pump l8 are driven. Preferably, the

pump I8 is arranged to receive the oil from a reservoir and/or metering chamber forming a part of the hydraulic unit I, and the discharge of the pump I8 is also directed through and controlled by parts in the unit I, as will now be described.

The hydraulic device I comprises an enclosing and supporting casing or housing 25 which, as indicated above, includes a metering cylinder 26 and a reservoir 21, the latter being closed by a cover plate 28. The lower and forwardmost portion of the unit 25 is formed to serve as a part of the pump l8, being provided with openings receiving three attaching bolts or cap screws 29 by which the casing 25 is held in place with a bore 3| formed therein, establishing communication between an inlet chamber 34 in the casing 28 and the intake or low pressure side of the pump l8, The outlet or high pressure side of the pump l8 connects with a bore 35 which joins a passageway 31 that is formed in the lower portion of the casing 25 and opens through a short cross bore 38 into a valve chamber 39. The high pressure duct 31 and associated parts are best shown in Figure 5. The valve chamber 39 communicates with the inlet chamber 34 through a pair of closely spaced openings 4|, as best shown in Figure l. The lower end of the casing is provided with an outlet 43 to which a hose fitting 44 is connected. The fitting 44 forms a part of a hose 45 that leads to the ram unit (Figure 1) described above. Formed in the casing 25 is an outlet passage 48 which at its outer end communicates with the outlet chamber 58 in the easingpart 43 under the control of a. valve 52 which opens outwardly but prevents flow of fluid inwardly, serving thereby as a check valve. The valve 52 is normally held in seated position by a spring 54 but may open outwardly when the pressure in the duct 48 exceeds the pressure in the chamber 54 and hose 45, and also when pressure is applied to the inner end of the stem 55 of the valve 52. The discharge duct 48 communicates with the valve chamber 39 through a cross bore 58, and the end of the duct 48 is formed as a valve seat which receives an emergency high pressure relief valve 58 that is normally pressed to the seat by a relatively heavy spring 59. The chamber 8| in which the spring and valve 58 are disposed opens into the metering chamber 25 through a port 62. The metering chamber 26 also communicates with a bore 85 (Figure 4) that extends downwardly through the housing 25 alongside the valve chamber 39 and which connects through a cross bore 68 with the lower or forward end of the valve chamber 39, ahead of the valve therein. Also, as best shown in Figure 4, the reservoir 21 in the housing 25 is in communication with the valve chamber 39 through a duct 61 and a cross bore 88 that leads into the central portion of the valve chamber 39.

The valve that is disposed in the valve chamber 39 is of the cylinder or plunger type and is indicated in its entirety by the reference numeral 18. The valve 18, as best shown in Figure 5, is formed with two plunger or cylindrical sections 1| and 12 connected by a narrow shank 13. The lower end of the cylindrical section 1| is formed with a cam end of generally curved configuration which cooperates with the stem 55 of the lowering valve 52, The valve chamber 39 opens at its upper end directly into the metering chamber 26, and the valve 18 includes a stem section 11 that extends upwardly into the metering chamber 26.

An operating member, indicated in its entirety by the reference numeral 88, is connected with the valve 18' and comprises an elongated stem 8| to the upper end of which a knob 82 is connected and the lower end of'which is threaded to receive the upper threaded end of the valve stem 11. A stop washer 83 is disposed between the lower end of the operating member 88 and a lock nut 84 that secures the valve 18 to the member 88 forming, in effect, a single part. A free piston 85 is disposed about the lower end of the stem 8| of the operating member 88 and, as best shown in Figure 5, the piston 85 comprises a guide bushing 88 and a packing bushing 81 between which a leather 88 is disposed. Packing 89 is disposed closely about the lower end of the stem BI, and the piston 85 is free to shift longitudinally of the lower portion of the stem 9|,

being limited in its downward movement by its contact with the stop washer 83. A light spring 98 may be used to urge the piston downwardly.

The upward movement of the free piston 85, which defines one wall of the metering chamber 28, is limited in an upward direction by an adjustable stop sleeve 9|, the interior of which is formed with a relatively large pitch thread 92, the sleeve 9| being in threaded engagement with a nut member 93 welded or otherwise firmly fixed to the stem 8| of the operating member 88. The sleeve 9| extends outwardly of the closure plate 28 of the reservoir 21 through packing means 95, and similar packing means 96 is carried by the upper end of the sleeve 9| and disposed about the stem 8 as best shown in Figure 3. The packing 95 is larger than the packing 98 and, if necessary, is tighter than the packing 96 whereby rotating the knob 82 while holding the latter against longitudinal movement in either direction acts through the threaded nut 93 and the threads 92 to cause the sleeve 9| to be advanced longitudinally inwardly or outwardly of the metering chamber 25. The lower end of the sleeve 9| is adapted to be contacted by the piston 85 when the latter reaches an upward position, as will be clear from Figure 1, and rotating the operating member 88 in one direction or the other relative to the sleeve 9| while restraining longitudinal movement of the member 88, changes the position of the lower end of the sleeve 9| so as to vary the capacity of the metering chamber 26.

The operation of this form of the invention is substantially as follows.

Figure 1 shows the parts in the position they occupy when the valve 18 is in its neutral position. This is the position in which fluid is locked in the ram 5, in which case the rock shaft l3 and associated parts (Figure 1) are held in position, which may be in a completely raised position or in any one of a plurality of intermediate raised positions, depending upon how much oil wa permitted to be withdrawn from the metering chamber 25 and forced by the pump l8 into the ram cylinder at high pressure. In this position of the valve 18, it will be noted that the cylindrical valve section 12 closes off the upper end of the cross bore 56, and the valve 52, being closed, also locks the fluid in the ram cylinder. If the operator should desire to lower the tools, he presses the operating member 88 directly inwardly, moving the same relative to the piston 85, because oil fills the metering chamber 26 below the piston. When the valve 10 is in its neutral position, oil is withdrawn from the inlet chamber 34 and the valve chamber 39 and passes through the pump l8, which is of a continuously operable type, the oil being discharged through the normally high pressure duct 31, the upper end of which opens directly back into the valve chamber 39, the entire circuit being under low pressure, as best shown in Figure 1. In this position of the valve, that is, the neutral position (Figure 1), the reservoir 21 is also in communication with the valve chamber 39 through the reservoir duct 61, 68, the cross bore 88 being so disposed, as best shown in Figure 1, that when the valve 18 is in a neutral position, the cylindrical section 1| thereof opens at least a portion of the reservoir duct 88 so that the latter is in communication with the valve chamber 39. Therefore, in the neutral position of the valve 18, the pump circulates oil that is in free communication with the supply of oil in the reservoir 21. This same idle circuit exists when the valve 18 is forced downwardly into its too] lowering position, as by the operator merely pressing downwardly on the knob. This forces the curved cam section 15 over the rounded end of the lowering valve stem 55, forcing the valve 52 to open and, at the same time, moving the valve section 12 downwardly to uncover the upper end of the port 56. Therefore, oil from the ram is free to flow past the open valve 52 and up through the ducts 48 and 56, past the valve stem I1 and into the metering chamber 26. This flow of oil takes place due to the weight of the tool or tools and/or assisting spring means where necessary, and as the oil flows into the metering chamber'26 the piston 85 rises or moves upwardly in the cylinder until it engages the lower end of the adjustable stop sleeve 8|. The piston 85 continues its movement, but since it is now in engagement with the sleeve 9!, that is connected with the valve operating member 8 I, the upward movement of the piston 85 now serves to restore the valve 18 to a neutral position, which permits the lower valve 52 to close and also closes the bore 56. It will be noted, also, that at any time during the lowering action, the operator may terminate the same, regardless as to whether the free piston 85 comes into contact with the lower end of the sleeve 9|, merely by pulling outwardly 0n the knob 82, which manually moves the valve 18 back into its neutral position. As mentioned above, by turning the knob 82 and shifting the latter to position the stop sleeve 9| in various positions, the amount of permissible lowering of the tools may be adjusted, as desired.

Assuming that it is desired to raise the tools, or extend the ram unit 5, whether-from their completely lowered position or from an intermediate position, all the operator has'to do is to pull out on the knob 82, thus raising the valve 18 into its raising position shown in Figure 5. It will be noted that in this position the cylindrical valve section 12 has been moved upwardly beyond the bore 56 and that the cylindrical valve section II has been moved upwardly into a position closing off the upper opening 4| and also -closing off communication between the valve chamber 39 and the reservoir ducts 61, 68.

Since the pump I 8 continuously operates, oil is withdrawn from the metering chamber 26 down through the low pressure passageway 65 and into the lower end of the valve chamber 39, below the lower end of the cylindrical valve section H The oil then fiowsout through the lowermost opening 4| into the intake chamber 34, and from there it enters the pump i8, being forced outwardly of the latter under relatively high pressure into the discharge ducts 38, 31, the upper end of the latter leading back into the valve chamber 39 but on the upper side of the cylindrical section 1 I. From this portion of the valve chamber 39, the oil flows under pressure through the cross bore 56, the duct 48, forcing the valve 52 open against the spring 54. Thus, oil is forced under pressure back to the ram 5, extending the piston 7 and swinging the rock shaft in a counterclockwise direction (Figure 1). The operator may terminnate the raising action at any time, merely by moving the knob 82 downwardly to dispose the valve 18 in a neutral position. However, the operator does not have to retain hold on the knob 82, for as the oil is withdrawn from the metering chamber 26 and forced by the pump l8 into the ram cylinder, the piston 85 follows the falling level of oil in the metering chamber 26 until the piston 85 engages the stop collar 83. Thereafter,

continued withdrawal of oil lowers the piston 85 and, by virtue of its contact with the stop washer 83, forces the valve 18 back from its raising position (Figure 5) into its neutral position (Figure 1). It will be noted that as the valve I8 moves from its upward position (Figure 5) back to its neutral position (Figure 1) the pump l8 stops pumping at about the time the valve section II starts to uncover the upper opening 4|, since a direct connection is now established between the intake chamber 34 and the discharge bore 31 directly across the valve chamber 38. Therefore,

the pressure falls and the pump can no longer do any work. The valve 18 tends to move downwardly under the action of gravity until its end 15 comes into contact with the inner end of the stem 55. However, there is no force available to force the valve 52 open, and hence it remains in its closed position.

If it should occur that, through leakage or the like, some liquid is lost from the system so that when the piston 85 moves downwardly its maximum amount the ram 5 has not been extended the desired amount, the system may be recharged in the neutral position of the valve by the operator grasping the valve 82 and pulling outwardly. Since the washer 83 is in contact with the lower portion of the piston 85, or substantially so, the operator lifts the piston 85 slightly. This alone tends to draw some liquid from the reservoir 21 past the leather 88 into the metering chamber 26, but in addition to this, the slight upward movement of the valve 18 causes the cylindrical section 'II to close off the upper opening 4|, thereby interrupting the direct connection between the discharge and intake portions of the pump. Therefore, the operation of the pump draws oil from the metering chamber 26, and oil that is drawn therefrom is replaced by the suction in the chamber 26 pulling oil past the leather 88.' Thus, as long as the operator holds the valve operating member 80 outwardly against the suction, oil is drawn from the reservoir 21 and forced to the ram 5. The operator may terminate the recharging action at any time merely by releasing his hold on the knob 82, whereupon the piston 85 engages the stop washer 83 and restores the valve 10 to its neutral or nonoperating position.

Another form of the present invention, employing substantially the same type ofstgalve mechanism and automatic cut-off described above and shown in Figures 1-5, is illustrated in Figure 6 et seq. In the first form of the invention, described above, the working ram unit 5 is extended or retracted by operating a valve controlling member, but once started in operation, the extension or retraction of the ram unit continues until the end of the cycle, which may be adjusted by disposing the stop sleeve 9| in different positions. In the modified form of the present inven-.

tion, to be described below, a slightly different type of control is provided, in which a manually operated control part may be moved into any one of a variety of positions, the mechanism functioning to extend or retract the ram cylinder a proportional amount. Y

Referring now to Figure 6 et seq. the reference numeral I 8| indicates the hydraulic metering chamber and valve unit in its entirety, which unit may be secured to the tractor 3 by fasten ing the same to the governor housing 2 in substantially the same manner as shown in Figure 1. A hose 45a leads from the operating and control unit I81 to a working ram unit 5'. Th unit 5' 7 is substantially the same as the unit 5, hence the parts thereof have been indicated by the same reference numerals to which primes are added for distinction. The operating and control unit I! comprises a casing I02 formed of a lower part I03 and an upper part or cover section I03a. The

\ lower section I03 includes a metering or control chamber or cylinder I04 in which a piston I05 is movable. A valve chamber I08 is formed alongside the cylinder I04, being somewhat more narrow as shown in Figure 7. The valve chamber I08 includes a cylindrical bore I09 in which a valve member H0 is movable generally longitudinally, A high pressure or pump outlet passageway II2 communicates with the cylinder I09 through a port I63, and a low pressure or pump inlet passageway II5 communicates with the upper portion of the valve cylinder I09 through a port I16. An outlet chamber II1 receives the hose 45a leading to the working ram and the outlet passageway H1 is controlled by a poppet valve I I8 having a stem I I9 that extends through a drilled passag in the wall I20 separating the high pressure passage I I2 from the valve cylinder I09. The inner end of the valve stem H9 is adapted to be controlled by the valve IIO, as will be described below, and a spring I22 acts against the valve II8 yieldingly urging the same toward its closed position.

The unit IOI includes a pump indicated in its entirety by the reference numeral I30 (Figure 7) and which includes a pump chamber I3I and a pair of gears I32 (Figure 6) adapted to be driven in any suitable manner by driving means that extends into the tractor governor housing 2. The discharge outlet of the pump is in communication with a cross bore II3 that extends into the high pressure passage II2 (Figure 6) and the intake of the pump is in communication with an intake or cross bore II6a that extends into the intake passage H5. The lower end of the latter connects with the lower end of the metering chamber through a port I38.

The valve H0 is a valve of the cylinder type, embodying an upper cylindrical section I which slides generally vertically in a sleeve section I42 carried at the upper end of the valve chamber or housing I08. The valve I I0 also includes a second cylindrical section I43 which is shiftable vertically in the central portion of the valve cylinder I09, having a lower pointed end I44. A small piston I46 iKslidable vertically in the lower portion I09a of the valve cylinder I09 and is biased for upward movement by a relatively stiff spring 1. The chamber I09a may communicate with the lower portion of the inlet passageway II5 through a port I48 which in the normal position of the parts is closed by the pressure control valve I46. The spring I41 preferably is arranged so that it does not expand farther than is shown in Figure 6. Hence, there is no tendency for the piston I46 to be forced upwardly by the spring beyond the position, just closing the port I49. If desired, however, an enclosing cage I45 may be provided, as is illustrated in Figure 11, in which both the spring and cage are free to follow the upward movement of the valve IIO, whereas in Figure 6, the plunger I46 is free to follow the upward movement of the valve H0 and the spring I41 may or may not, depending on whether the spring remains or is fixed in the bottom of the chamber I09a, Or is fixed to the plunger I46. The

latter construction is preferable. In either form,

the spring, I41 or I41, is compressed whenever the valve H0 is moved downwardly. Above the lower portion I09a of the valve cylinder I 09, in which the cylindrical valve plunger I46 is disposed, is an annular chamber I5I which com municates through a bore I52 with the lower portion of the high pressure passage I I2. The lower end of the latter is closedby a wall I 53 in which a port I54 is formed. The lower portion of the port serves as a valve seat to receive a high pressure emergency relief valve I55. The valve I55 is normally held in closed position by a relatively strong spring I60 which is disposed in a spring chamber I56, the chamber I56 communicating with the lower portion of the valve chamber I09 through a port I51. The lower ends of the valve chamber I09 and spring chamber I56 are closed by screw threaded plugs I58 and I59, respectively. The valve IIO, between the cylindrical sections MI and I43 thereof, is reduced in diameter, as indicated at I6I, the upper portion of the reduced shank I6I being connected with the upper section I by a tapered or conical portion I62 which is normally disposed in an annular chamber I63 leading into the upper end of the high pressure chamber H2. The lower end of the shank I6I is connected with the lower cylindrical section I43 by a portion I65 that is of curved or cam cross section, this being the portion that cooperates with the outlet valve stem H9, as will be described below in connection with the operation of the device.

The position of the valve I I0 in the valve chamber I09 is controlled by linkage that differentially connects the piston I05 and an operating handle I10 with the valve, the linkage being indicated in P its entirety by the reference numeral Ill and being disposed in an upper chamber I12 formed by the upper or cover section I03a of the unit I0 I. The upper end of the valve I I0 extends out of the valve housing I08 and into the chamber I12, the upper end being bifurcated, as indicated at H3, and carrying a pin I14 to which one end of a lever I15 is pivotally connected. The other end of the lever I15 is connected by a link I16 with the upper end of a piston rod I11, the lower end of which passes through an opening I18 in a guide disk I19 which extends across the upper portion of the cylinder I04. The guide disk I19 is provided with a plurality of openings I84 so that there is a free flow of fluid between the cylinder I04, above the piston I05, and the chamber 812. The lower end of the rod I11 is provided with a shoulder I8I against which the piston I05 is disposed.

The piston I05 comprises a backing member I9I which is formed with a central boss section I92 apcrtured to receive the reduced end I93 of the piston rod I11. A piston leather I94 is disposed against the backing member I9I and is normally held with its edges against the walls of the cylinder I04 by a snap ring I95 or other suitable means. The end I 93 of the piston rod I11 is threaded, as at I96, and over the threaded end is disposed a clamping plate member I91, the latter being held in place by a lock washer I98 and a clamping nut I99.

The piston I05 includes biased valve means providing for a replenishing flow of fluid into the space below the piston I05, and such valve means is indicated in its entiret by the reference numeral 20I. The valve means comprises a plurality of valves, each of which includes a ball 202', a biasing spring 203, both being disposed in a bore 204 formed in the section I92 of the backing member I9I. The clamping disk I91 serves to retain the springs 203 in position and is formed with a plurality of opening 201 which are in communication with the bores 204, whereby under conditions where replenishment is necessary, fluid may flow through the valves 202 and into the space below the piston I05.

Referring again to the linkage Hi, the intermediate portion of the lever I15 is connected by a link 2I0 with an arm 2 fixed to a shaft 2I2,

one end of which extends into the chamber I12.-

The shaft 2I2 is supported for rocking movement in a bearing boss 2I3 that extends into the casing I12, the outer end of the shaft 2 I2 being fixed .to the operating handle I10 by a pin M or other suitable means. The link I16 is formed with an apertured portion 22I to which the upper end of a spring 222 is connected. The lower end of the spring 722 is anchored to an apertured boss 223 providedon or carried by the guide disk I10.

As described above, the operating handle I is fixed to the outer end of the shaft 2I2. An adjustable sector 23I is pivotally mounted on the rock shaft 2| 2 between the lever I10 and the adjacent side of the cover housing I03a. The sector 23I is formed with a notch 232 having diverging walls 234 and 235, and an extension 236 is carried by the sector and has a slot 231 that extends generally longitudinally of the extension 23*. A cap screw 24I' is threaded into an apertured boss 242 formed onone side of the cover I-73a. A spring 243 is disposed under the head of the cap screw 24I and bears against a plate or disk 244 which is formed with a stop abutment 245 and an inwardly extending tongue or lug 245 that lies in the slot 231. The function of the tongue or lug 246 is to prevent the disk 244 from turning on the cap screw 2. Therefore the stop 245 is held in position. The'sector 23I is extended, as at 236a, so that the detent 249, described below, never rides off the sector 23I in any position of the latter and the handle I10. A

stop 241 is formed on or carried by the casing I030. to limit the rearward movement of the handle I10.

A pivoted detent dog 249 is swingably mounted on a pin 25I carried by the hand lever. I10 and is provided with a detent section 252 at one .end and an aperture 253 at the other end. A rod 254 has one end engaged in the aperture 253. The rod extends along the hand lever I10 and at its other end is threaded, as at 255, into a ball 256 that is mounted for sliding movement on the upper end of the hand lever I10. A spring 258 serves as biasing means for holding the ball in its out-er position. When pressed inwardly, the ball acts through the rod 254 to swing the detent dog 249. Normally. the detent section 252 rides along the u per edge of the sector 23I and its extension 236, the detent section 252 being suffic ently wide to engage the lug 245 on the disk 244. The notch 232 and the stop lug 245cooperate with the detent dog 252 for determining two end positions of movement of the hand lever I10, and this position may be adjusted when desired by engaging the detent section 252 in the notch 23 and then pulling outwardly on the ball 256 so as 'to hold the detent 248 against swinging movement. Tlfien by shifting the handle in one direction or the other the sector remains locked to the handle and may be pivoted about the rock shaft 2I2 so as to bring the notch 232 closer to or further away from the cooperating stop lug 245. It will be noted that the spring 243 acts through the disk 244 for frictionally holding the sector 23I in a position in which it is set as in the manner just described.

10 The operation of this form of the invention is substantially as follows.

In the position shown in Figures 6 and 8, the sector 23I is set in a position for maximum lowering, and in Figure 6 the position of the metering or control piston I05 isthat which it occupies when all of the oil in the ram cylinder hasbeen returned to the control unit IOI, which places the ram piston in its most retracted or maximum lowered position, as best shown in Figure 6.

Assuming that the operator desires to raise the implement part to its fully raised position, the operator pushes forwardly on the control handle I10, in a counterclockwise direction as viewed. in Figure 6 and in a clockwise direction as viewed in Figure 8. Since the cylinder or control chamber I04 is filled with oil, the forward movement of the handle, I10 causes counterclockwise movement of the rock shaft 2I2 (Figure 6), the downward pull on the link 2I0 acting to swing the lever I15 in a clockwise direction about its pivotal connection with the upper end of the link I15. This "moves the valve member IIO downwardly, which downward movement forces the plunger I46 down against the pressure of the spring I41, clearing the lower part I090 of the valve chamber I09 of oil. If the handle I10 is moved all the way forwardly, the lower end I44 of the valve moves down to approximately the position shown in dotted lines in Figure 6. The downward movement of the valve I I0 causes the upper cylindrical portion I42 of the. valve H0 to close 01! communication between the port I03 and the port I6. A moment after this port is closed the pump discharge port H3, and this, causes oil to force the popp t valve IIO open and to flow through the hose a to the ram cylinder 6'. The

, oil that is pumped into the ram cylinder 5' is withdrawn from the control chamber I04, and as the oil is withdrawn the spring 222 causes the piston; I05 to followdownwardly as the oil flows out of the'chamber I04. This downward movement of the piston tends to swing the link I15 in a counterclockwise direction about its pivot connection with the upper end of the link 210, which would act to raise the valve IIO. This upward movement of the valve I I0, which begins immediately, accommodates the expansion of the spring I41 by an amount corresponding to the free length of the spring I41 (Figure 6), or corresponding to the movement permitted by the cage I45 (Figure 11). The further and continued upward movement of the valve IIO merely causes the piston I46 to follow the valve IIO; Oil below the valve IIO therefore never interferes with movement of the valve.

Under the conditions assumed, wherein the operator moved the handle I10 to its forwardmost position, the downward movement of the piston I05 does not open the ports I83 and I52 until all of the oil has been withdrawn from the chamber I04 and the piston '1' of the ram unit 5' moved into its fully extended position, which corresponds to the position of the ram ,shown in Figure 1.

As a matter of actual practice, as soon as the operator moves the handle I10 forwardly only a slight amount, the valve H0 closes the ports I03 and I52 so that the pump starts forcing oil under pressure to the ramv even before the operator moves the lever I10 into its forwardmost position. It may be considered, therefore, that as the 0D- erator moves the handle I10 forwardly, the operation of the pump in withdrawing oil from the control chamber I04 causes the piston I05 to move downwardly, under the action of the spring 222, the downward movement of the piston and the forward movement of the control handle I10 occurring more or less simultaneously, However, so long as the handle I10 ls ahead of the piston I05, the valve H will be held in its lower position and the ram will therefore receive oil under pressure from the pump, this action continuing until the piston I moves downwardly to the bottom of the control chamber, against the pad 280, at which time the disposition of the handle I with its detent dog 249 adjacent the stop lug 245 serves to cause the last part of the movement of the piston to the lower portion of the chamber I04 to move the valve I I0 upwardly. As soon as the lower edge of the cylindrical valve part I43 starts toopen the port I52, the upper port I63 being still closed, there is a rush of oil under normal or operating pressure from the high pressure chamber II2 into the chamber I09a underneath the valve I I0. This pressure, which is limited by the spring I41 or I41, therefore acts immediately to complete the upward opening movementof the valve IIO, moving the handle I10 back a slight amount. The completion of the valve opening movement by the normal working pressure in the system secures a positive and definite opening of the ports I63 and I52 for terminating the delivery of oilunder pressure to the ram cylinder when the control piston I05 reaches a predetermined point.

It is to be noted at this time that if the operator does not desire to lift the tools to the maximum extent, he may lift them to any extent dedesired merely by moving the hand lever I10 forwardly out otits lowered position (full lines, Figure 6) into some intermediate position: If the control lever I10 is left in some intermediate position, thedownward movement of the piston I05 as oil is withdrawn from the control chamber I04 and delivered by the pump under pressure to the ram cylinder, will raise the valve IIO back to its neutral position (Figure 6) at a point in the downward travel of the piston I 05 that corresponds to the intermediate position in which the control lever I10 is disposed. Therefore at this intermediate point the pump will automatically stop delivering oil under pressure to the ram and will merely be driven idly. If the operator desires to raise the tools an additional slight amount, all that he has to do is to move the lever I10 forwardly a corresponding increment, the first movement of the lever I10 in a forward direction momentarily lowering the control valve I I0, which initiates the delivery of oil under pressure to the ram, but as the oil is delivered the piston I05 moves downwardly and then will automatically terminate the delivery of oil under pressure to the ram in a second position corresponding to the new position to which the hand lever I10 moved. The present mechanism therefore functions as a servo-motor, having a part which may be moved through any number of steps and into an infinite variety of positions, the operating unit functioning to deliver oil under pressure to extend a ram by practically exactly corresponding amounts, the extension of the ram automatically terminating merely by leaving the handle I10 in any given or desired position. Ordinarily, however, for agricultural implement purposes, the tools usually are raised the maximum amount, which means that the control lever ll!) will be thrown forwardly to its maximum extent. with the detent 249 in engagement with the stop lug 245.

It should also be noted at this point that, with the hand lever I10 left in, say, an intermediate position, the downward movement of the piston I05 as oil is withdrawn from the control chamber and delivered to the ram gradually raises the valve H0. The parts are so constructed and arranged that the lower portion of the cylinder section I4I starts to open-the port I63 a slight distance after the cylindrical section I43 starts to open the lower port I52. That is to say, the downward movement of the piston I05 in causing the upward movement of the valve I I0 first opens the lower port I52 while the upper port I63 is still closed. Since the discharge chamber II2 contains oil under pressure, just as soon as there is even a slight opening at the lower port I52, oil under pressure flows through such slight opening and into the space below the lower end I44 of the valve H0. There is created, therefore, below the valve IIO a zone of fluid under pressure which acts almost instantaneously to complete the upward movement of the valve IIO, quickly opening the upper port I63 and thereby permitting the discharge of the pump to communicate directly with the intake. The space below the lower end I44 of the valve H0 is defined at its lower portion by the movable plunger I46. This member normally closes the port I48 that communicates with the intake of the pump and the lower portion of the control chamber I04, being held in this position by a spring I41. This spring is relatively light but is capable of exerting suflicient force so that the momentary surge of pressure through the slightly open port I52 is sufllcient to complete the upward movement of the valve before the oil begins to flow through the space below the valve I I0 and forces the plunger I48 downwardly, thereby opening the ,port I48 and permitting oil to flow directly from the discharge chamber I I2 of the pump into the control chamber I04. The port I51 between th high pressure relief valve chamber I56 and the space below the valve IIO is so constructed and arranged that even in the lowermost position of the valve IIO, there is always communication between the chamber I56 and the lower portion of the valve chamber I09. Therefore, if at any time during any part of the extension of the ram the latter should become jammed or there is for any reason excess pressure developed in the system, the relief valve I55 may open and divert such abnormal pressure through the chamber I56 and the port I51 into the space below the valve IIO. This excess pressur immediately forces the plunger I45 downwardly, opening the port I48 and permitting the excess quantity of oil to flow into the chamber I04, thereby relieving such abnormal load. There may be no actual flow of oil into the chamber I04, since the opening of the emergency relief valve I55 and the downward movement of the plunger I46 merely places the discharge port I I3 of the pump in direct communication, through the ports I51 and I48, with the intake IIBa of the pump. The pump therefore idles and is not required to be driven under load.

The operation of lowering the tools will now be described. Lowering the tools requires that the oil that is locked in the ram cylinder and associated parts by the valve H8 be permitted to flow back to the control chamber I04. The valve II8 may be opened by swinging the hand the tension of the spring I 22.

13 lever I10 rearwardly, or to the right as viewed in Figure 6. This causes clockwise movement of the rock shaft 2I2, and since normally the left end (Figure 6) of the link H5 is held against upward movement bythe spring 222, such clockwise movement of the arm 2II acts through the link 2I0 and the link I'I5 to raise the valve H0. This brings the curved or cam portion I05 of the valve IIO into action against the inner end of the stem II9, the upward movement of the valve thus forcing the valve I I8 open against the valve II8 opens oil from the ram cylinder is then permitted to flow through the port I63 and the port II6' into the valve intake chamber II5, from whence it may flow into the control chamber I04 through the port I38. Normally, the path of movement of the oil as just described is adequate to conduct all oil from the ram cylinder into the control chamber. However, if there should be excessive load on the tools, the oil may flow downwardly through the port I52 and into the lower portion of the chamber I09, forcing the plunger I46 downwardly and opening the port I48, whereupon oil may flow from the discharge chamber H2 and join the oil entering the control chamber I04. As the oil flows into the control chamber I04 the piston I05 rises, and this upward movement acts through the link I'I5 to move the latter in a clockwise direction about its pivot connection with the upper end of the link 2I0. such movement tending to shift the valveIIO downwardly into its neutral position. However, the pressure of the spring I22 and the flow of oil past the valve IIB acts against the stem [I9 to hold it quite firmly against the side of the valve H0, so that instead of the valve H0 moving downwardly the handle is caused to move downwardly as the piston I05 rises, since the resistance to movement of the handle in this direction is less than the resistanc to the downward movement of the valve I I0. Therefore, the lowering movement of the tools will continue until the handle is stopped in its movement. The handle may be stopped, however, by the operator grasping the same and momentarily holding it in position, but preferably the sector 23I is arranged so as to dispose th notch 232 ina position to be engaged by'the detent dog section 252 at the desired lowered position of the tools, the last increment of raising. of the piston I05 acting to move the control valve IIO back to its neutral position. This movement of the valve II 0 by oil pressure and the corresponding movement of the lever H0 is accommodated by the length of the notch 232,

The walls of the notch 233 are arranged to be divergent so that the handle I'I0 may, if desired, be moved past the notch in either direction without interference, although when the detent engages in the notch, further movement of the handle by the oil entering under the piston I05 is ffectively prevented. To secure this action,

the tension of the spring 243 must create a hold-' ing force resisting displacement of the sector 23I that is greater thanthe tendency for the spring 258, holding the detent 252 in the notch 233, to cause displacement of the sector 23I when the handle is forcibly moved past the notch 233 in either direction.

, The function of the spring 222 is two-fold. First, it acts to maintain the joints of the linkage III tight and takes out all slack, and furthermore, the spring 222 acts to hold the piston I05 down against the oilwith a pressure that However, when v serves to hold the balls 202 up against the valve seats, thereby preventing oil from flowing from underneath the piston I05 up. into the upper part of the unit I'0I above the piston I05. This upper part of the unit IOI serves as a reservoir, and normally the oil level therein is high enough to maintain a substantial reservoir of oil. As in the form of the invention described above, the control chamber I04 and the cylinder of the ram unit, together with associated connections, form a closed hydraulic circuit. In the present construction, the oil in the control chamber and ram cylinder may be replenished by pushing down on the ball 256, whichraises the detent out of engagement with the stop lug 245. Then the lever I10 may be moved forwardly an additional amount, which lowers the valve IIO and closes the ports I63 and I52. The pump therefore starts to withdraw oil from below the piston I05 and delivers it to the ram. However, since the control piston I05 cannot move downwardly any farther, oil is drawn past the leather I94 of the piston I05 from the quantity of oil above the piston I05, thus serving as an additional supply of oil which is directed to the ram by the operation of the pump so long as the handle I10 is moved forwardly past the lug I45 Therefore, as soon as the ram has been extend ed to the desired amount, the handle H0 is restored to its normal position and the delivery of oil to the ram cylinder is then terminated, and at the same time the system is replenished and is ready for normal operation. Not only is the oil drawn past the leather I94 as just dey scribed, but also oil flows past the valves 202.

The upper portion of the casing I03a is provided with a filler plug 300 of the filter type, including filtering means 30L This permits the oil level in the upper part of the unit IOI to rise and fall but without drawing in objectionable amounts of dirt and the like. By removing the plug 300 the oilin the upper part, or reservoir, of the unit IOI may be replenished from time to time as may be necessary. Also, the unit IOI may be charged in the first instance by having the pistonv I05 in its lowermost position in the chamber I04 and then pouring oil into the unit IOI through the hole in which the filler plug 300 is normally disposed. The springs 203 are chosen so that the additional head of oil causes the balls 202 to move away from their seats, and a quantity of oil, sufficient to prime the pump I32, flows through the piston valves 20I and fills the pump passages. The pump is started and then the handle I10 is swung rearwardly to move the valve IIO down to close off the ports I63 and I52. The pump will then draw oil from above the piston I05 past the leather I94 and the valve 202 and into the system.

In initially charging the unit, it is preferable to charges the system with the correct amount of oil.

Figure 9 shows an optional arrangement in which the control unit is not necessarily fixed to the tractor so as to be operated by the governor mechanism but may be placed on the tractor in any suitable position, deriving its operating energy from a separate pump that may be driven from any suitable actuating part of the tractor and not necessarily from the governor mechanism, as in the arrangement shown in Figure '7.

draulic-control unit- Hlla, which maybe mounted on the traotor'3b in any suitable manner, as by brackets 3| 1; and in any suitable location, as desired; Preferably, the hose 314 is connected to communicate directly with the inlet port of the pump, corresponding to the intake port H6 shown in Figure 6 for the unit i 9 -A second hose 3i8 is connected with'the discharge port of the pump 310 and'extends upwardly to the unit lola and is in direct communication with the discharge port of the'unit I'Dla, such'port corresponding with the discharge port H3 shown in Figure 6. In other respects, the control unit lDla shown in Figure 9 is constructed exactly as shown and described above in connection with the control unit IOI shown in Figure'fi, so that further description is unnecessary, except to "say that a hose 3I9 is connected with the discharge chamber H10. of the unit llila and leads to-a ram unit (not shown) that'rnay belocated atany desired point, either onthetractor 3b or on an implement connected to or propelled thereby; The arrangement shown in Figure 9 may therefore be attached to any suitable tractor and may have the pump 3| I driven from the tractor by any suitable manner, not only from the power take-oil shaft 310 as illustrated, but also by some other connection, such as a belt pulley, or other shafting or gearing and the like. The pump 3l lmay be mounted on and driven from the implement, also. I

Another form of thepresent invention is illus-' trated'in Figure 10. In this form hydraulic control valve mechanismis employed which is substantially'the same as shown in Figure 6 but the control chamber has been eliminated and the valve cont-rolling linkage connected. directly to the part that raises and lowers the implement tools. Referring now to Figure 10, it will be noted that the control mechanism of the present invention is illustrated as; embodied in a tractor power lift similar to that shown in the patent to Elmer McCormick et al., No. 2,107,760, dated February 8, 1938, to which reference may be made if necessary; In this form of the invention the tractor is indicated by the reference numeral 30, the tractor bein represented largely by the banjo portion of the rear axle housing 33!. The tractor 30 also includes a power take-off shaft 332 which drives the two gears 333 and 334 of a gear pump indicated in its entirety by the reference numeral 335. Preferably, the pump is constructed substantiall as shown in the McCormick et al. patent, the pump gears 333 and 334 being disposed in a pump housing 336 that is bolted against the rear face of the power lift housing 331, the latter being fixed to and closin the rear opening of the rear axle banjo section 33L The power lift housing 331 isformed to include a reservoir R and a vertically extending cored section 338 in which a passage 339 is formed, the passage 339 communicating at its lower end with the high pressure side of the pump 335. A low pressure passage 34! leads from the-reservoir R directly to the low pressure side of the pump 335, this construction being quite similar to that shown in the McCormick et al. patent.

The power lift housing 331 includes bearings (not shown) in which a lifting rock shaft 345 is 16 supported for rocking movement, and fixed generally to the central portion of the rock shaft 346 is an arm 346 that extends in a generally downward direction and at its lower end is connected by a pivot pin 341 with a link 348, the forward end of the latter being pivoted, as at 349, to a piston 35| operating in 'a. cylinder 352' bolted, as at 354, to the front side of the power lift housing 331. An opening in the front wall of the latter accommodates the disposition of the link 348 and its extension into the cylinder 352. The cylinder 352 communicates at its forward end with a passageway 356 that extends from the front end of the cylinder rearwardly, and the passageway 356 registers with a passageway 351 formed in a tubular portion 358 that extends across from the front wall to the rear wall of the power lift housing 331. Implement tools or other part or parts to be. actuated are connected in the usual way with the ends of the rock shaft 345.

In this form of the invention the valve mechanism is indicated in its entirety by the reference numeral 365, the valve mechanism including a valve casing 366 having a cylindrical bore 361 in which a valve 368 is disposed for vertical movement. As in the form of the invention shown in Figure 6, the valve 368 includes an upper cylindrical section 369 and a lower cylindrical section 31l, and the lower portion of the cylindrical valve receiving bore 361 communicates with the lower portion of an outlet or discharge high pressure chamber 312. This chamber communicates with the upper end of the high pressure passageway 339 through a bore 313. A low pressure passage 314 communicates with the upper portion of the cylindrical bore 361 through a port 316, and the lower portion of the low pressure passageway 314 communicates with the reservoir B through a. bore 316 and the passage 34!. A high pressure emergency relief valve 319 is constructed substantially like the safety valve "55 described above, the chamber 331 in which the valve 318' is disposed communicating with the space below the valve 368 through an elongated port 382. A plunger valve 383 backed by a relatively stiff spring 384 is disposed in the lower portion of the cylindrical valve receivin bore 361 and controls a port 385 which opens communication between the bores 361 and 314. The discharge chamber 312 is adapted to communicate with the passageway 351 through a valve controlled port 386. The valve is indicated at 369 and includes a stem 3 extending across the chamber 312 and into a position to be operated by the curved or cam section 392 of the valve 368. A spring 393 bears against the valve 389 and normally holds the same in closed position. The spring 384 may, if desired, be replaced by the type of preloaded spring shown in Figure 11.

The valve 366 is controlled by linkage which operates in substantially the same manner as the linkage l1! shown in Figure 6. The operating linkage for the valve 368, which is indicated in its entirety by the reference numeral 460, comprises a bell crank 40! pivoted at one end, as at 402, to the upper end of the valve 368. The other end of the ball crank, which is offset laterally to clear the bored part of the casing 366 in which the upper end of the valve 368 slides, is connected by a. pivot pin 484 to a generally forwardly and upwardly extending link 405 that is pivoted at its forward end on a pin 408 on the power lift rock shaft arm 346. A hand lever a, of substantially the same construction as the hand lever I10 shown in Figure 6, is connected at its lower end to a rock 17 shaft 4! I that extends through the casing 366 and at its inner end receives an arm H2. The latter is connected by a link 3 to the lever 40!.

It will be observed that the linkage just de scribed is disposed in substantially the same relation as'the linkage l1l shown in Figure 6, the

principal difference being that in Figure 6 the linkage ill connects a control piston I with the valve and operating handle, whereas in Figure 10 the linkage 400 connects the power lift arm 346 with the control handle l'ifla and the valve 358.

In both forms, however, for any given position of the hand lever, H0 or I'Hla, a part movable in j responseto the extension of the'associated ram unit serves to automatically return the valve to its neutral position. In Figure 6, the piston I05 normally moves with the extension of the ram,

inf response to the extension of the ram. Both thepiston Hi5 and the power lift rock shaft arm 346, as a matter of fact, move concomitantly with 'tli'e tool or tools associated therewith.

Yi fI'he. operation of the form of the invention I ,'and associated parts which are constructed sub- "stantially' exactly like the corresponding parts shown inFigure 7. When the hand lever l'lfla. is moved, for example, in the raising direction,

"the valve 368 is lowered until the port 313 is closed, whereupon the pump delivers oil under pressure to the cylinder 352 through the passageways 351 and 355. The piston 35! moves outwardly in response to the delivery of oil to the ,"c'ylinder" 352, rocking the'arm 346 and the rock shaft 345. Thecorresponding movement of the arm 346'acts through the linkage 400 to return the valve 368 to its neutral position. Therefore,

' as in the form of the invention shown in Figure 6, the hand lever lllla may be moved to any position along its sector and left in that position, and the operating mechanism will automatically rock the rock shaft 345 a corresponding amount, holding the rock shaft in a position corresponding to the position in which the hand lever l'llla is left. Ordinarily, the hand lever "(la is moved into its fully raised position, which results in the power lift arm 345 swinging rearwardly the full extent before automatically returning the valve 368 to its neutral position. When lowering, the hand lever Him is moved rearwardly, and the resulting forward swinging movement of the power lift arm 346 will automatically move the hand lever IlOa rearwardly until its detent engages the associated notch in the sector 231a. The position of the sector 23la may be adjusted in substantially the same manner as described above in connection with the sector 23L While'I have shown and described above the preferred means in which the principles of the present invention have been incorporated, it is to be understood that my invention is not to be limited to the particular means shown and described above, but that, in fact, widely different means may be employed in the practice of the broader aspects of my invention.

What I claim, therefore, and desire to secure by Letters Patent is:

1. In an agricultural machine, power lift mechanism comprising a ram unit including a ram cylinder, a power driven pump,. a chamber, fluid connections between said pump, chamber and ram cylinder, valv means controlling the while in Figure 10 the rock shaft arm 346 moves i i 4 i flow of fluid through said connections, and movable into a position for accommodating a flow of fluid from said ram cylinder to said chamber, means operatively connected with said valve means for manually shifting the latter, and means in said chamber responsive to the quantity of fluid in said chamber and reacting against said manually shiftable means for moving said valve means into a position terminating said flow.

2. Hydraulic power lift mechanism for agricultural implements and the like, comprising a working ram unit including a cylinder and a piston therein, a fluid pump, a metering cylinder, operative connections between said pump, metering cylinder and ram cylinder, a valve controlling said connections and movable in one direction from an intermediate position locking fluid in said ram cylinder and movable in the other direction from said intermediate position, a movable piston in said metering chamber and defining one wall thereof, said piston moving to different positions in the metering cylinder in response to the quantity of fluid therein, manually operable means for shifting said valve means in either direction from said intermediate position, and means responsive to movement of the piston in said metering cylinder for shifting said manually operable means and said valve means into an intermediate position from either of their other positions.

3. In a hydraulic system, a single acting ram unit including a cylinder and a piston movable therein in response to flow of fluid into and out of one end of said cylinder, valve means controlling the flow of fluid to and from said end of said cylinder, 3, metering device including a chamber having a movable wall, a pump having a suction inlet and a pressure outlet, fluid connections extending between said pump inlet and said cylinder and valve, fluid connections extending between said pump'outlet and said valve and chamber for supplying fluid to the inlet of said pump, and adapted to receive fluid from said ram, valve means movable from a neutral position, in which said pump is by-passed to said chamber, into a position for controlling the flow of fluid from th ram to said chamber, means for moving said valve means into said one opera tive position, and means responsive to the flow of a given quantity of fluid to said chamber for moving said valve means from said one operative position into its neutral position.

5. In an agricultural implement having a part to be shifted from one position into a number of other positions, a working ram unit for controlling the position of said implement part and including a cylinder and a piston movable therein, a fluid pump, a metering cylinder having a piston movable therein and defining one wall of a metering chamber formed by the metering cylinder, connections between said metering chamber, said fluid pump and said ram cylinder to accommodate a flow of fluid from the metering chamber through the pump and into the ram cylinder 21 thereby holding the piston thereof in extended position, means for moving said valve means out of said third' position into either of its other metering chamber having a piston movable therein and defining one wall thereof, valve controlled ports connecting said pressure increasing device, ram cylinder and metering chamber, valve means controlling said ports and movable into one position in which fluid is withdrawn from said metering chamber and delivered under pressure to said ram cylinder and movable into another position in which fluid flows from said ram cylinder back to said metering chamber and bypassing said pressure increasing device whereby fluid from said ram cylinder flows back into said metering chamber, said valve means being movable into a third position in which fluid is locked in said ram cylinder, thereby holdingthe piston thereof in extended position, means for moving said valve means out of said third position into either of its other positions, and means responsive to movement of the piston in said metering chamber in response to flow of fluid to said chamber from said ram cylinder and adjustably connected with said valve means for shifting the latter automatically into its third position from said other position when a given quantity of fluid has entered said metering chamber, said quantity varying according to the adjustment of said responsive means.

14. In an agricultural machine having a part to be shifted from one position to another, a hydraulic ram connected with said part to shift the same, means for supplying fluid under pressure to said ram to extend the latter and shift said part in one direction, means providing for the flow of fluid out of said ram and the retraction of the ram to shift said part in the other direction, valve means shiftable to control the flow of fluid between said two means and said ram, a second part movable in accordance with the movement of said first part, manual control means connected difierentially with said second part and said valve means whereby continuous or interrupted movement of the latter effects continuous or interrupted movement, respectively, of said first part, means whereby when fluid flows from said ram said valve means is held against .movement and said manual control means is moved by the action of said differential connection, and mechanism for restricting further movement of said manual control means, whereby said difierential connection acts to shift said valve means.

15. The invention set forth in claim 14, further characterized by means for adjusting said mechanism so as to change the point at which restriction to further movement of said manual control means is encountered.

16. In a hydraulic system, a chamber, a fluid pump, a working ram unit having a ram cylinder and a ram piston movable therein, a valve controlled passageway from said ram cylinder to said chamber, a valve controlled passageway leading from .the discharge side of said pump around to the intake side thereof and communieating with said chamber, means including a check valve placing said last mentioned passageway in communication with said ram cylinder, a shiftable valve controlling saidfirst two mentioned passageways whereby in one position of the valve member fluid 'under pressure is forced past said check valve into said ram cylinder and movement of said valve member in the other direction opening said second passageway and closing said first passageway, whereby fluid circulates in an idle circuit through said pump in communication with the chamber, an additional movement of said shiftable valve member in said other direction serving to open said check valve while leaving said second valve controlled passageway open, and means responsive to the quantity of liquid in said chamber for controlling said shiftable valve member.

17. In an agricultural machine, power lift mechanism comprising a ram unit including a ram cylinder, a power driven pump, a chamber,

fluid connections between said pump, chamber and ram cylinder, valve means controlling the flow of fluid through said connections, and mov= able from a neutral position into one position for accommodating a flow of fluid from said ram cylinder to said chamber and into another position providing for a flow of fluid from said chamber through said pump to said ram cylinder, means operatively connected with said valve means for manually shifting the latter from said neutral position to said one position and to said other position, optionally, and means in said chamber responsive to changes in the quantity of fluid in said chamber and reacting against said manually shiftable means for moving said valve means back to said neutral position from either said one position or said other position.

- FRANK T. COURT.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,017,557 Kieser Feb. 13, 1912 1,855,434 Vickers Apr. 26, 1932 2,229,561 -Galanot Jan. 21, 1941 1,907,208 Lebel May 2, 1933 1,775,856 Hauser Sept. 16,1930 2,114,157 Towson Apr. 12, 1938 2,229,530 South Jan. 21, 1941 2,311,516 Brown Feb. 16, 1943 2,243,364 Trautman May 27, 1941 2,293,071 Morgensen Aug. 18, 1942 1,016,573 Maddox Feb. 6, 1912 2,072,088 Dysart Mar. 2, 1937 1,806,136 Weiss May 19, 1931 1,968,422 Proctor July 31, 1934 1,940,508 Proctor Dec. 19, 1933 2,264,560 Albertson Dec. 2, 1941v 1,897,386 Ferris Feb, 14, 1933 1,058,271 Sundh Apr. 8, 1913 1,206,707 Hunter Nov. 28, 1916 2,114,005 Tyler Apr. 12, 1938 2,342,450 Campbell Feb. 22, 1944 2,165,966 Hall -July 11, 1939 2,192,963 Davis Mar. 12, 1940 1,955,154 Temple Apr. 17, 1934 FOREIGN PATENTS Number Country Date 558,460 Great Britain 1944 

